Hello
I modeled a connecting pin that is mounted in a screed.
By simulation in Solidworks I model surfaces to allow me to apply the different loads.
Under Rdm7 I used the optimization tool to get closer to the values.
My axis at the base is 6 mm for a stress of 100 MPA.
How can we faithfully translate the initial conditions under the solidworks module.
Thank you in advance.
Good evening
This is not the right way to proceed!
You have to use the bearing connectors
We won't talk about it tomorrow
Kind regards
Hello
The bearing connector is giving me trouble...
I have the phenomenon of great displacements that start, I refuse and here are my results.
I modified the 3D model by leaving a circular surface on 360° at the level of the contacts.
Thank you for your help, have a good day and have a good weekend.
Hello
For the bearing connectors you need to have the bearings, but here you only have the shaft. So nothing holds your piece, which is why it goes all the way to the Bermuda Triangle.
The bearing can be represented by a simple plate with a hole without backlash with the shaft. This must be done in an ASM and not in a single room (SLDPRT) if you want to have a correct result. The bearings must be fixed and the shaft constrained in the axis with the contact that goes well (look in the choices proposed).
Also remove your grooves in all directions and replace them with dividing lines . This makes it possible to separate areas without altering the structure by removing material. I made a tutorial on the subject https://www.lynkoa.com/contenu/les-lignes-de-s%C3%A9paration-1.
Indeed, if you reduce your material removals as a percentage, you induce inaccuracies before you start
Obviously you need a landing on each side of the tree! and all in an ASM
Kind regards
Hello
Ok, thank you very much, I'm taking everything back with the right instructions.
So I'm modeling in an assembly and I'll post my results.
Kind regards;
Hello
So I modeled 2 bearings at the nominal dimension, no adjustment or mechanical play.
I have made separation lines through successive planes that intersect the fractional zone (4 zones).
The solid is subjected to two supports, I consider the initial load out of two, i.e. 380 N.
Then it drifts a little........ The dialog box requires an axis guide.
I can't define this auxiliary marker.
Is it necessary to go through a 3D sketch which will allow a new direct sorting
or is it not necessary?
I respected the instructions given, to connect the axis of revolution with the axis marked Z on my sketch, then for the Y axis it is my flat external face, on the other hand for the X axis no anomaly to hang on my model.
so I'd like to know if I can use a 3D sketch to get this third axis.
Thank you for your help.
Hello
Can you send the assembly and the part back but using the pack and Go function (accessible from File)
Otherwise ASM doesn't work. Return the latest version of the axis with the separation lines.
In the anf Go pack don't forget to put the result of your simulations (a box to check)
Kind regards
For coordinate system you have a function designed for this
Insertion==> reference geometry==>coordinate system From there, the three axes are easy to position, especially on a cylinder that is centered on the three main planes, which means ideally positioned for the coordinate system
Kind regards
Hello
Ok thanks for the auxiliary cue.
I have made both loading landings.
One of the rooms must be masked to access the desired surface.
The coordinate system is selected.
I'm sending you the Pack and GO.
Thank you for your assistance on this dedicated connector.
Hello
An error in the definition of the Z-axis...........
The problem is the infinite distance, I'll change to see the incidence.
"set of faces of the same radius"..........
A cylinder is defined by flat surfaces (axial stop for example, shoulder or collar, here I have the Z axis as the generator of the cylinder.
Here's my pack and Go.
Thank you.
Oops I have an error on the cutting of my areas, I consulted a doc from your forum,
"Separation of the face A dividing line must be created on the face in such a way as to define the half-space in which the load is applied. "
So I'm going to first isolate my contact ring with the bearing and then limit myself to 180 degrees. , to get closer to the contact conditions.
Coordinate system complement, example quote.
Coordinate system A coordinate system must be created in the center of the face. Condition to be met: The Z axis must be along the face (the Z axis is confused with the axis of the cylindrical face).
The line that splits my ring into two parts will become the selection edge.
I'll test.
And here is my V1 simulation, with a load of 380N per 1/2 step.
Hello
If you don't put your ASM in a "pack and GO" including your simulation results you won't get any additional comments ;-) ;-)
I see that you have made quite a bit of progress since our first exchanges.
Kind regards
Hello
I tried to apply the indicated approach.
I'm amazed by the contributions of the simulation part and the very extensive options.
You will find the Pack and Go attached.
For the moment the material is not definitive, it is a first draft to rough up this connector.
Thank you for all the advice, have a good day.
P.S:
There is little video illustration of this connector or the indexing is difficult to find.
Hello
A few comments
1°) You have not defined any material for your simulation. I don't even understand how you can get a result in this case (normally SW sends you on a trip to the Parthenon) So I arbitrarily put an alloy steel 1.7139 (16MnCr55) S235JR
2°) In your simulation you simulated the load on the bearings themselves but you did not apply a bearing load on the axis itself. I probably wasn't explicit enough, sorry!
Remark on point 1°
The bearing load allows you to calculate the load on the 2 bearings, which you have done. But as it seems to me that you talked about piston (or more precisely clevis shear) you have to calculate a bearing load on the shaft itself with a load of 760 N: having obviously removed the other two bearing loads from the bearings.
It all depends on whether you want to test the pads or the axle itself when it's in position. It's the same approach but not quite the same result, for the axis itself.
General Note
I strongly suggested that you use the bearing load because the calculation is not the same as a beastly force applied vertically which would be wrong. Look at the online help on the criterion "Bearing load" and you will see the two main modes of distribution, namely: sinusoidal variation and parabolic distribution.
2°) you don't exploit all the possibilities of SW analysis which means that you can be surprised (but probably not surprised enough in my opinion)
To be perhaps more surprised and comforted at the same time, you would have to ask in the results
1°) the calculation of the safety factor
2°) Design dissection. (see attached image) This is interesting because it allows you to have an internal vision of the part. Indeed, whether it is "Von mises" or "Displacements", you have an external vision of matter. As it is not possible to have a cross-sectional view of the simulation, SolidWorks offers something more sophisticated, which is a vision of the internal loading levels of the material with the possibility of a fine analysis of the most loaded areas to the least loaded areas (very fine and very easy to use adjustment).
Regarding the safety factor, it comes out in my simulation at 2.69 in the most constrained zone, but higher than 5 on the rest of the set. This is consistent with the manual calculation which comes out in CS 4.37 for a pure shear force (i.e. shear force when you are not in screed).
PS: why are you talking about connectors (what is your axle for?)
Kind regards
Hello
Thank you for your explanations, don't be sorry, I'm the one who has to adapt to the simulation tool, which I admit without difficulty.
The dissection of conception, I didn't know, missing the box, not very serious........ to be disseminated because it is additional information.
For the subject I may have deleted after the first simulation, for a change.
Solidworks does not do calculations, it must be fed with known forces and then it exploits, it does not isolate the parts.
I removed the bearing loads, I loaded the axis on 1/2 cylinder in relation to the separation line, how is the transfer carried out at the level of the two bearings two separation lines exist, I left it as it is.
Here is my capture with the design dissection contribution but my values are different from yours, I missed something I think. The volumes are well distributed on both sides of the axis.
The bearing connector rejects me if I don't reverse the direction......... strange.
No influence on the result.
My shaft / piston is a project to validate a modus operandi.
I'm going to do this on a scaled down to observe in use.
Attached is an Excel file to calculate the Hertz pressure.
Have a nice weekend.
